EP0515307B1 - Einrichtung zum Steuern des Auslassventils einer Hubkolbenbrennkraftmaschine - Google Patents

Einrichtung zum Steuern des Auslassventils einer Hubkolbenbrennkraftmaschine Download PDF

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Publication number
EP0515307B1
EP0515307B1 EP92810309A EP92810309A EP0515307B1 EP 0515307 B1 EP0515307 B1 EP 0515307B1 EP 92810309 A EP92810309 A EP 92810309A EP 92810309 A EP92810309 A EP 92810309A EP 0515307 B1 EP0515307 B1 EP 0515307B1
Authority
EP
European Patent Office
Prior art keywords
piston
exhaust valve
cylinder
control piston
channel
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP92810309A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0515307A1 (de
Inventor
Robert Hofer
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Winterthur Gas and Diesel AG
Original Assignee
Winterthur Gas and Diesel AG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Winterthur Gas and Diesel AG filed Critical Winterthur Gas and Diesel AG
Publication of EP0515307A1 publication Critical patent/EP0515307A1/de
Application granted granted Critical
Publication of EP0515307B1 publication Critical patent/EP0515307B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L9/00—Valve-gear or valve arrangements actuated non-mechanically
    • F01L9/10—Valve-gear or valve arrangements actuated non-mechanically by fluid means, e.g. hydraulic
    • F01L9/11—Valve-gear or valve arrangements actuated non-mechanically by fluid means, e.g. hydraulic in which the action of a cam is being transmitted to a valve by a liquid column
    • F01L9/12—Valve-gear or valve arrangements actuated non-mechanically by fluid means, e.g. hydraulic in which the action of a cam is being transmitted to a valve by a liquid column with a liquid chamber between a piston actuated by a cam and a piston acting on a valve stem
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L13/00—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L9/00—Valve-gear or valve arrangements actuated non-mechanically
    • F01L9/10—Valve-gear or valve arrangements actuated non-mechanically by fluid means, e.g. hydraulic
    • F01L9/11—Valve-gear or valve arrangements actuated non-mechanically by fluid means, e.g. hydraulic in which the action of a cam is being transmitted to a valve by a liquid column
    • F01L9/12—Valve-gear or valve arrangements actuated non-mechanically by fluid means, e.g. hydraulic in which the action of a cam is being transmitted to a valve by a liquid column with a liquid chamber between a piston actuated by a cam and a piston acting on a valve stem
    • F01L9/14—Valve-gear or valve arrangements actuated non-mechanically by fluid means, e.g. hydraulic in which the action of a cam is being transmitted to a valve by a liquid column with a liquid chamber between a piston actuated by a cam and a piston acting on a valve stem the volume of the chamber being variable, e.g. for varying the lift or the timing of a valve

Definitions

  • the invention relates to a device for controlling the exhaust valve of a reciprocating piston internal combustion engine with the features of the preamble of claim 1.
  • a device with these features, which is also intended for controlling intake valves, is known from FR-A-2 436 255.
  • the pressure of the pressure medium which opens the inlet and / or the outlet valve and thus the time at which the valve opens and closes are dependent on the shape of the cam driving the stroke transmitter on the camshaft.
  • the line containing the pressure medium column is designed as an upside-down U and the drain channel is connected at the highest point of the U.
  • pressure medium is released via the open throttle point during the entire time that the cam is being moved by the cam, as a result of which the course of the valve movement deviates from the cam shape.
  • the invention has for its object to improve a control device of the type mentioned in such a way that the closing time of the exhaust valve can be varied in a structurally simple manner, and that it can be brought forward compared to the closing time determined by the cam shape, without the opening time being changed at the same time .
  • the opening time of the exhaust valve always remains the same and the opening speed of the cam shape correspondingly high, on the other hand the exhaust valve reaches the closing time earlier than determined by the cam shape.
  • This causes a change in the compression pressure and thus also the ignition pressure, which can now be kept constant in the upper part of the load range.
  • This possibility also makes it possible to improve the fuel consumption in this part-load operation of the internal combustion engine.
  • the throttle cross-section in the discharge duct is adjusted depending on the load.
  • a working piston 2 is arranged in a working cylinder 1 of a 2-stroke diesel internal combustion engine up and down.
  • the working piston 2 is connected via a piston rod, not shown, to a crosshead, which is articulated in a known manner on the crank pin of a crankshaft via a push rod.
  • a cylinder head 3 which delimits a combustion chamber 7.
  • a housing part 4 is inserted, which contains an exhaust duct 8 in its lower section.
  • a seat surface 5 is formed which interacts with an exhaust valve 9.
  • purge air slots 10 In the wall of the working cylinder 1 there are several purge air slots 10, only one of which is shown in FIG.
  • the scavenging air slots are connected to a scavenging air chamber 11, from which scavenging air enters the combustion chamber 7 via the scavenging air slots 10 when the working piston 2 with its upper boundary edge has cleared the scavenging air slots 10 during the downward stroke.
  • the then entering purge air pushes the combustion gases into the exhaust duct 8 via the open exhaust valve 9, whereupon the air compresses during the upward stroke and with the exhaust valve 9 closed when the upper edge of the working piston 2 has passed the purge air slots 10.
  • at least one fuel injector is arranged in a known manner, which in the region of the top dead center of the Working piston 2 injected diesel oil into the compressed air in combustion chamber 7.
  • a servo piston 12 is arranged, which is guided in a cylinder 13 of the housing part 4.
  • a compressed air line 15, which contains a throttle 14, is connected to the cylinder space located in FIG. 1 below the servo piston 12.
  • the air enclosed in this way in the cylinder space below the servo piston 12 forms an air spring which acts on the exhaust valve 9 in a closing sense.
  • the servo piston 12 protrudes with its upper end in FIG. 1 into a cylinder space 19, to which a line 20 is connected, which opens into a cylinder space 63 of a control device 68, which is arranged separately from the internal combustion engine.
  • the cylinder chamber 19, the line 20 and the cylinder chamber 63 are filled with a hydraulic pressure medium, for example oil.
  • a control piston 62 is guided in the cylinder space 63 and is supported on the upper end of a stroke transmitter 61.
  • the stroke transmitter 61 is provided at its lower end in FIG. 1 with a roller 22 which is supported on a cam 23 'of a camshaft 23.
  • the line 20 is filled by means of a pump 24 with the hydraulic pressure medium, which is sucked in from a tank 25 and is conveyed into the line 20 via a line 26 with a check valve 27 with a pressure between, for example, 8 and 16 bar.
  • a conduit 65 branches off from the line 26 and opens into the cylinder space 63, at the level of the upper end face of the control piston 62 in FIG. 1, which is in its lowest position in the position shown .
  • An overpressure valve 24 ' is also arranged in a known manner on the delivery side of the pump 24.
  • a vent line 54 leading to the tank 25 is connected to a throttle point.
  • the control piston 62 is provided with three piston rings 64 arranged distributed over its length.
  • an outlet channel 66 branches off from the latter, which leads via a shoulder 67 'to a space 67 into which a movably guided throttle pin 69 projects.
  • a line 34 is connected to the space 67 and leads to the tank 25.
  • An axial channel 70 extends from the upper end face of the control piston 62 in FIG. 1 and opens with its lower end into an annular groove 71 which is arranged in the lower half of the control piston 62.
  • the annular groove 71 is arranged on the control piston 62 so that it is in the uppermost position of the control piston in front of the mouth of the discharge channel 66, the control piston 62 shutting off the mouth of the channel 65 with its outer surface located above the annular groove 71.
  • the discharge channel 66 is expediently given one of the three cross sections shown in FIG. 1a, the triangular-like cross section on the outside on the right being the best in order to avoid vacuum formation in the cylinder space 63 when the control piston 62 moves downward.
  • the position of the throttle pin 69 relative to the shoulder 67 ' is dependent on a controller 78, to which an electrical signal corresponding to the flushing pressure is supplied via the signal line 58 and an electrical signal corresponding to the setpoint of the closing time of the exhaust valve 9 via a signal line 59.
  • the one corresponding to the flushing pressure Signal is representative of the engine load.
  • the controller 78 is connected via two pressure medium lines 72 and 73 to an actuating cylinder 74, in which an actuating piston 75 is movably guided.
  • the piston 75 is articulated to a lever 76 of an eccentric shaft 77, on the eccentric 79 of which a pivot lever 80 is supported.
  • the controller 78 adjusts the eccentric 79 via the actuating piston 75, as a result of which the pivoting lever 80 is adjusted about the articulation point 81, which results in a displacement of the throttle pin 69 and thus the throttling effect.
  • a pivotable cam 82 is also operatively connected to the eccentric shaft 77 and in turn interacts with a fuel regulating linkage 83.
  • the cam disk 82 acts as a load limitation for the internal combustion engine.
  • the stroke curve of the control piston 62 is plotted over the time axis B and two stroke curves of the exhaust valve 9 are plotted over the identical time axis C, specifically with the solid line D the stroke curve when using the invention and with the dashed line E the stroke curve without application the invention.
  • the point F on the axis B lies at about 100 ° crank angle before UT and at point R (about 80 ° before UT) on the axis C the opening of the exhaust valve 9 begins because the roller 22 runs onto the cam 23 '.
  • the annular groove 71 on the control piston 62 reaches the discharge channel 66 and then remains in front of it until it leaves the mouth of the discharge channel again between the points K and M. It starts at point H on axis C. Discharge of pressure medium via the discharge channel 66, as a result of which the outlet valve 9 - in deviation from the curve (dashed line E) given by the shape of the cam 23 '- begins the movement curve according to curve D.
  • the outlet valve 9 is again in the closed position, ie approximately 10 ° crank angle before point P, namely the closing time which would be given by the shape of the cam 23 '.
  • the point N can be both closer to point P and closer to UT.
  • the greatest distance between point N and point P is approximately 50 °.
  • Fig.1 works as follows: In the drawn position of the camshaft 23, the working piston 2 is in the area of the top dead center.
  • the outlet valve 9 is opened after the roller 22 of the stroke transmitter 61 runs onto the cam 23 ′ and the control piston 62 has passed the mouth of the channel 65, so that the pressure medium column in the line 20 is displaced towards the cylinder chamber 19. As a result of this displacement, the outlet valve 9 is moved in an opening sense. As soon as the upper boundary edge of the annular groove 71 on the control piston 62 in FIG.
  • the pressure medium volume of the column in line 20 is replenished by pump 24 via line 26 after the annular groove 71 has passed the mouth of the discharge channel 66 during the downward stroke of the control piston 62.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)
  • Valve-Gear Or Valve Arrangements (AREA)
EP92810309A 1991-05-22 1992-04-28 Einrichtung zum Steuern des Auslassventils einer Hubkolbenbrennkraftmaschine Expired - Lifetime EP0515307B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CH1521/91A CH681825A5 (xx) 1991-05-22 1991-05-22
CH1521/91 1991-05-22

Publications (2)

Publication Number Publication Date
EP0515307A1 EP0515307A1 (de) 1992-11-25
EP0515307B1 true EP0515307B1 (de) 1995-01-04

Family

ID=4212391

Family Applications (1)

Application Number Title Priority Date Filing Date
EP92810309A Expired - Lifetime EP0515307B1 (de) 1991-05-22 1992-04-28 Einrichtung zum Steuern des Auslassventils einer Hubkolbenbrennkraftmaschine

Country Status (6)

Country Link
EP (1) EP0515307B1 (xx)
JP (1) JP3416165B2 (xx)
KR (1) KR100267599B1 (xx)
CH (1) CH681825A5 (xx)
DE (1) DE59201118D1 (xx)
DK (1) DK0515307T3 (xx)

Families Citing this family (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE59205027D1 (de) * 1992-08-06 1996-02-22 New Sulzer Diesel Ag Verwendung einer Vorrichtung zum Zurückhalten von festen Teilchen in einem Fluidstrom
US5857438A (en) * 1997-03-18 1999-01-12 Barnard; Daniel Wayne Hydraulically operated variable valve control mechanism
DK0959240T3 (da) * 1998-05-22 2003-10-27 Waertsilae Nsd Schweiz Ag Cylinderdæksel til en totakts-dieselforbrændingskraftmaskine og anordning indeholdende en sådan
GB2410060A (en) * 2004-01-14 2005-07-20 Lotus Car A two-stroke compression-ignition internal combustion engine
WO2010006599A1 (en) * 2008-07-14 2010-01-21 Man Diesel Filial Af Man Diesel Se, Tyskland Cam driven exhaust valve actuation system for large two stroke diesel engine
ES2376927B1 (es) * 2009-03-27 2013-02-04 Josep Poblet Fortuny Motor de explosión de combustión interna.
EP2500550A1 (en) * 2011-03-16 2012-09-19 Siemens Aktiengesellschaft Stroke transmitter for gas turbine
FI123759B (en) * 2012-03-09 2013-10-31 Waertsilae Finland Oy Ventilaktuatorarrangemang
JP6141209B2 (ja) * 2014-01-10 2017-06-07 三菱重工業株式会社 排気弁駆動装置およびこれを備えた内燃機関
JP6293636B2 (ja) * 2014-10-08 2018-03-14 三菱重工業株式会社 排気弁駆動装置およびこれを備えた内燃機関
JP6254245B2 (ja) * 2016-12-05 2017-12-27 三菱重工業株式会社 排気弁駆動装置およびこれを備えた内燃機関

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2785667A (en) * 1953-11-18 1957-03-19 Nordberg Manufacturing Co Hydraulic mechanism for actuating an engine valve with variable timing
FR2287583A1 (fr) * 1974-10-10 1976-05-07 Maschf Augsburg Nuernberg Ag Dispositif de commande hydraulique reglable de soupape
FR2436255A1 (fr) * 1978-09-16 1980-04-11 Maschf Augsburg Nuernberg Ag Dispositif hydraulique pour la commande de soupapes controlant le passage de gaz

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH01134018A (ja) * 1987-11-19 1989-05-26 Honda Motor Co Ltd 内燃機関の動弁装置
DE3815668A1 (de) * 1988-05-07 1989-11-16 Bosch Gmbh Robert Ventilsteuervorrichtung mit magnetventil fuer brennkraftmaschinen
DE3834882A1 (de) * 1988-10-13 1990-04-19 Bosch Gmbh Robert Ventilsteuervorrichtung fuer brennkraftmaschinen

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2785667A (en) * 1953-11-18 1957-03-19 Nordberg Manufacturing Co Hydraulic mechanism for actuating an engine valve with variable timing
FR2287583A1 (fr) * 1974-10-10 1976-05-07 Maschf Augsburg Nuernberg Ag Dispositif de commande hydraulique reglable de soupape
FR2436255A1 (fr) * 1978-09-16 1980-04-11 Maschf Augsburg Nuernberg Ag Dispositif hydraulique pour la commande de soupapes controlant le passage de gaz

Also Published As

Publication number Publication date
KR920021838A (ko) 1992-12-18
JPH05156912A (ja) 1993-06-22
CH681825A5 (xx) 1993-05-28
KR100267599B1 (ko) 2000-10-16
DE59201118D1 (de) 1995-02-16
DK0515307T3 (da) 1995-03-13
JP3416165B2 (ja) 2003-06-16
EP0515307A1 (de) 1992-11-25

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